JPS59211703A - Low-temperature engine device - Google Patents

Abstract

An improved engine system is provided which includes a synthetic low temperature sink that is developed in conjunction with an absorbtion-refrigeration subsystem (23) having inputs from an external low-grade heat energy supply (21) and from an external source of cooling fluid (24). A low temperature engine is included which has a high temperature end (22) that is in heat exchange communication with the external heat energy source (21) and a low temperature end (36) in heat exchange communication with the synthetic sink provided by the absorbtion-refrigeration subsystem (23). By this invention, it is possible to vary the sink temperature as desired, including temperatures that are lower than ambient temperatures such as that of the external cooling source. This feature enables the use of an external heat input source that is of a very low grade because an advantageously low heat sink temperature can be selected.

Description

DETAILED DESCRIPTION OF THE INVENTION This application is a continuation-in-part of U.S. Patent Application No. 400,464, filed June 21, 1982.

TECHNICAL FIELD The present invention relates generally to engine systems, and more particularly, operates at significantly lower temperatures when compared to high pressure, high temperature engine systems, such as high pressure turbines used in facilities with low temperature turbines and associated steam turbine power plants. The present invention relates to an engine device. A low-temperature engine device that can replace such a low-temperature turbine is
Combined with a synthetic heat sink that can create a cooler fluid flow than typical external cooling sources operating at ambient temperatures.

In response to the recognition of the increasing non-renewable nature of excavated fuel resources, solar energy, ocean thermal gradient energy, geothermal energy potential, biomass and other lower grade renewable fuel sources can be used. Attention has increasingly been turned to various technologies that have the potential for the development of low-grade energy sources such as devices. Little attention is paid by the general public to the utilization of the amount of waste heat energy released into processing environments that consume high-grade fuels.

Of course, increasing the efficiency of equipment that consumes high-grade fuel,
Alternatively, it is desirable to provide equipment that uses low-grade energy sources to conserve natural resources.

One attempt to increase such efficiency is to convert waste heat energy into usable energy such as electricity. For example, in the electricity industry, a significant amount of heat is dissipated by being released from the condensers of steam turbines. Furthermore, the haphazard release of this waste heat into the surrounding environment has raised strong concerns regarding thermal pollution. Over the past few years, attempts have been made to recover some of this thermal energy. Past attempts have focused on dual steam engine systems, including systems with coupled gas turbine/steam cycles or engine systems with a bottoming cycle low temperature turbine added in series to the discharge end of the steam turbine cycle. It consisted of equipment collaborated with Rankine Cycles.

Attempts along this line are to transfer waste heat from a single steam turbine cycle to a large volume of water that is readily available at outside temperature.
These attempts are to discharge directly into the suction, typically on the order of 1 inch I (P), at the lowest practical condensing pressure or high vacuum conditions.
It still needs to release the residual heat of condensation. It often happens that this heat is more than twice the practical heat actually converted into useful power by the turbine during the cycle.

Attempts have been made to improve this situation by modifying the cold portion of the cycle by using halogenated carbon coolants as the thermodynamic medium rather than steam. This approach considerably improves the overall thermodynamic efficiency of all steam, while also eliminating the need for high vacuum condensation pressures. Overall thermodynamic efficiency is improved because the coolant vapor is lower in temperature than water vapor. This means that the waste heat released during liquefaction of the thermodynamic medium is reduced with respect to the unit heat available in the cycle.

Although this effort has resulted in considerable improvements, attempts to further increase the efficiency of this system are inherently limited by the temperature of the low-grade heat source proposed to provide heat input and the cycle is subject to inherent constraints because the minimum temperature at the bottom end of the cooling system is dictated by the temperature of the uncontrollable naturally occurring cooling source. Such efficiency is the term calc cycle efficiency, which is a function of the difference between the temperature at the heat source or top end of the cycle and the temperature at the bottom end of the cycle or the “sink” of heat created by the naturally occurring body of the fluid. As defined, that limits the theoretical maximum potential efficiency of any system.

Certain prior attempts have been to increase the temperature differential of the calc cycle by discharging waste heat into a suction that does not occur naturally and is lower than the temperature of the naturally occurring body. These attempts rely on preparing and placing a cold cooling bath in a storage location until the need arises for the chilled fluid to be withdrawn from the reservoir for use in reducing the condenser temperature. Vapor compression cooling is used in this regard. This cooling will require more input shaft power to provide the cooling needed to provide the suction that becomes available as the shaft power output increases. The shaft power output provides limited efficiency gains. These attempts are based on 6" batches where energy is stored for later use.
characterized as a device. However, the amount of energy recovered from such storage will typically be less than the amount of energy expended to perform the storage.

Therefore, there is considerable benefit to be gained in providing a heat release suction in connection with a low temperature engine where the suction can most effectively be varied in temperature up to a temperature below that of typically available natural objects. There is. A further significant advantage is that this suction can be provided in a form other than a suction of a stored batch of energy.

These goals are achieved in accordance with the present invention by providing a low engine system with a continuous flow synthetic suction that is developed concurrently with the operation of the engine system. The only external inputs required are a low grade heat source and an ambient temperature fluid source. A low temperature engine arrangement according to the invention includes a low temperature engine coupled in heat exchange relationship with said low grade thermal energy input. The low temperature heat engine is coupled in heat exchange relationship with an absorption-cooling subsystem having an absorber arrangement coupled in heat exchange relationship with an external cooling source at ambient temperature.

The heat exchange temperature between the continuous flow synthetic suction and the low temperature heat engine will be below the ambient temperature of the external cooling source.

Accordingly, it is an object of the present invention to provide an improved low temperature engine system.

Another object of the invention is to provide an engine arrangement that is substantially independent of the availability of stored auxiliary energy equipment.

Another object of the present invention is to provide a continuous flow synthetic suction that consumes energy at a lower rate than the increased power output yield resulting from its use in conjunction with an overall cold engine system.

Another object of the present invention is to provide a useful engine system in response to concerns regarding thermal pollution.

Another object of the invention is to provide a low temperature engine system with increased low temperature turbine output and reduced rotating machinery and capital costs.

Another object of the invention is to reduce the net energy consumption in the cooling cycle to the point where the net energy input is lower than that required to offset the benefits of increased power to the turbine cycle. Accordingly, it is an object of the present invention to provide an engine device capable of regenerating heating and cooling between an engine cycle and a cooling cycle.

Another object of the invention is to provide an engine system that combines various elements to achieve an interaction that increases the overall efficiency of the engine system.

Another object of the present invention is to provide an improved low temperature engine that operates without the need for input shaft power and that cooperates with an absorption-cooling subsystem that uses thermal energy as the input energy source.

Another object of the present invention is to provide an improved low temperature engine system that is compatible with continuous flow synthetic suction having a suction temperature lower than ambient air and in which the suction temperature can be selected as a variable design parameter.

The low temperature engine system according to the invention consists of a low grade thermal energy input source 21, a low temperature heat engine 22, and absorption-cooling subsystems 23I23a, 23b. External cooling#
24 is in heat exchange connection with the absorption-cooling subsystem. The external cooling source 24 is ultimately predominantly water-based, although other structures, usually mechanically assisted, may be included as well in providing the external cooling source 24.

Low grade thermal energy input source 21 may be any one of a number of heat sources. The heat source creates a heat source at a higher temperature than the temperature at which the thermodynamic medium of the cryogenic heat engine 22 enters the cryogenic heat engine 22 at an appropriate pressure. Such energy input sources 21 include the output of solar collectors, heated cooling water from various industrial facilities, low grade fuel burners, and the like.

For convenience of explanation, the lower energy input supply 'm21 is illustrated here as waste heat discharge from another thermal engine cycle operating at a higher temperature than the cold engine system of the present invention. In this connection, the low grade thermal energy input source 21 is illustrated as a steam turbine 25 having a high temperature, high pressure steam power 26 and a steam outlet 27 . A steam turbine 2 in which steam pressure and humidity drive a generator 28, etc.
Steam passes through the steam outlet 27 after being reduced by the work done in operating 5.

For convenience of illustration, the low temperature heat engine 22 is shown as a single turbine operated by a closed Rankine cycle. Low temperature heat engine 22, unlike steam turbine 25, uses thermodynamic media other than steam, such as nitrogenated carbon coolant, imbutane, ammonia, and combinations thereof. Illustrated low temperature heat engine 2
2 drives a generator 29 and the like.

The absorption-cooling sub-device 26 is a low-grade thermal energy manual power supply source 2
Simultaneously and in conjunction with the release of heat from the steam outlet 27 through the steam outlet 27, the continuous flow secondary fresh air cup 1 degree heat intake is combined.

The absorption-cooling subsystem 26 contains a solution of a mixture of absorbent and coolant. This absorption-cooling solution is a combination of two fluids. One has particularly useful absorption properties, and the other has cooling properties. Water is often used as an absorbent. Other absorbents include dimethyl ether of tetraethylene glycol, lithium bromide, and the like. The coolant is ammonia, water,
Contains halogenated hydrocarbons. special absorption
Cooling solutions may vary from one particular cold engine device to another. Determining which choice is appropriate depends on considerations such as the intended peak temperature of the heat input source, the intended low temperature of the suction conditions to be synthesized,
These include the characteristics of the external cooling source 24, desired operating pressure management within the system, economic considerations as well as considerations such as toxicity, corrosivity, flammability of the solution, etc.

In all embodiments of the present invention, a low temperature heat engine 22 and The associated engine cycle and the associated absorption-cooling cycle with the absorption-cooling subsystem 23 interact primarily through heat exchange interaction.

More specifically, within the absorption-cooling subsystem 26, the cooled heat engine medium is immediately phase heated to repeat the cycle as a heat engine medium. The cold medium from the cold heat engine serves as a coolant for the waste heat released by the absorption-cooling subsystem 26. Due to the interaction of these gods, thermal energy is transferred within the entire cold engine system and the waste heat to be released is significantly reduced. All of this is accomplished while simultaneously providing a synthetic suction that is cooler than the outside air to accommodate the temperature difference between the heat input temperature and the heat rejection temperature.

Steam passes through steam outlet 27 to provide heat input to the low temperature engine system according to the invention.

The heat input is both a low temperature heat engine cycle and an absorption-cooling subsystem cycle. This is achieved in the embodiment shown in FIGS. 1 and 2 by branching the steam exhaust conduit into two lines 31, 32. This steam is transferred to a bag that has completed heat exchange bonding.
It is cooled and typically condensed. At that time, a return pump 3 for returning the steam to the steam boiler (not shown)
This is because the low temperature engine device is exited through 6.

In further detailing the heat exchange coupling between steam turbine 25 and the cold heat engine cycle, steam from steam turbine 25 enters steam condenser 34 having a suitable heat transfer member 65. The thermodynamic medium of the cold heat engine 22 circulates through the heat transfer member 35 as part of the flow path for the cold heat engine cycle. This special heat exchange coupling completes the increase in temperature of the heat engine thermodynamic medium before it enters the cold heat engine 22.

The thus heated and compressed thermodynamic medium is expanded through the cryogenic heat engine 22 to low pressure conditions and to a significantly reduced temperature below the ambient temperature of the external cooling source 24. do.

When the thermodynamic medium leaves the cold heat engine 22 through the outlet 66, it becomes a cold low pressure vapor suitable for σ) which enters the absorption-cooling subsystem 26.

In the embodiment of FIGS. 1 and 2, this heat exchange coupling is provided to absorber 67 which is coupled in heat exchange relationship with condenser/evaporator 68. Heat is provided in the condenser/evaporator 68 to the point at which the cold vapor of the thermodynamic turbine medium leaves the condenser/evaporator 58 and passes through the outlet conduit 39 so that it is condensed to a liquid. Heat provided by the thermodynamic turbine medium is added to the coolant of the absorption-cooling subsystem it23.

With particular reference to the embodiment of FIG. The water is circulated with the help of a pump 41 so as to create a passage.

Such temperature increase is facilitated as the thermodynamic medium passes through the steam condenser 54n heat transfer member 65 to complete the heat engine cycle. In addition to providing regenerative energy to the thermodynamic medium, the heat exchange coupling of the condenser 42 allows the refrigerant 42 to enter the condenser 42 to the extent that it leaves as vapor at the inlet 46 through the outlet 44 in a liquid state. to cool the coolant.

To further explain the details of the absorption-cooling subsystem 26, this particular embodiment includes an absorber 67, a condenser/evaporator 3
8, a heat exchanger or condenser 42, and a generator 45. Heat is input from the low grade thermal energy source 21 to the absorption-cooling subsystem 26 through the line 62 previously described. This extracted steam is used to heat the contents of generator 45.

The cooler vapor is returned to vapor condenser 64 to complete condensation before passing through return pump 63 if necessary. This heat transfer to generator 45 partially distills the cooling of the absorption-cooling solution within generator 45. This evaporated coolant passes through condenser 42 to perform the heat exchange described above. This liquefies the evaporated coolant as it leaves the outlet 44 and also increases the heat and temperature of the thermodynamic medium as it flows through the condenser 42 .

The coolant passing through outlet 44 is now in liquid form but at an elevated pressure relative to the passage through expansion valve 46 . The expansion valve 46 allows the thermodynamic medium to enter the condenser/evaporator 68.
The refrigerant passes through the condenser/evaporator 68 at the temperature required to combine the suction conditions imposed on the medium as it passes through the condenser/evaporator 68.
Upon entry, the pressure of the liquid coolant is reduced to facilitate instantaneous evaporation. The refrigerant is in the condenser/evaporator 38
Upon leaving the expansion valve 46 and entering the absorber 67, the coolant absorbs the heat of condensation rejected by the thermodynamic medium and its temperature is slightly increased from the temperature after leaving the expansion valve 46.

In the absorber 67, the coolant is preferably mixed by spraying a warm absorbent weak solution of the absorbent-cooling bath liquid. This mixing combines the refrigerant and absorbent as an absorbent-cooling solution at a higher temperature than that typically provided to absorber 67 by heat transfer element 47 by external cooling #I 24. This reduces the absorption-cooling solution to a temperature equal to or slightly above the temperature of the external cooling source 24 while the cooling fluid is returned to the external cooling source 24 by return conduit 48 . This feature of cooling the absorption-cooling solution within the absorber 67 facilitates the solution forming process and also allows higher concentrations of coolant to decompose within the absorber than would occur in an uncooled environment.

The shaped strong absorption-cooling solution is sent to the supplementary heat exchanger 51 with the aid of a cooling circulation pump 49. in this case,
The solution is warmed by hot weak solution absorbent flowing from generator 45 after partially distilling this absorption-cooling solution into vaporized coolant and heated liquid absorbent. Generator 45
The increased pressure exerted on the heated absorbent in
It is reduced to the lower operating pressure of absorbent 67 by passing through supplementary heat exchanger 41 and passing through pressure reducing valve or jet 52 .

This completes the absorption-cooling cycle. The fluid in the condenser 42 and generator 45 becomes highly compressed, and the fluid in the absorber 6
7 and the fluid in condenser/evaporator 68 is at reduced pressure. Modifications to the absorption configuration are made to achieve the desired more constant pressure. With the cycle completed in this way, the heat of condensation of the coolant in the absorption-cooling cycle is rejected from the cold engine system to the outside, but it is used for regenerative heating of the thermodynamic medium.

FIG. 2 illustrates an embodiment that makes it possible to further reduce the net waste heat rejected from a cold engine arrangement according to the invention, in particular the waste heat rejected through the return conduit 4B. Under proper conditions, the cooling fluid returned to the external cooling source 24 can approach the temperature of the external cooling source 24.

This is accomplished by increasing the heat exchange interaction of the cooling fluid with the absorption-cooling subsystem 26 and by adding heat exchange interaction with the thermodynamic medium. This embodiment shows that after the thermodynamic medium passes from condenser/evaporator 38 through conduit 69 and pump 41 to condenser 42,
Assistance occurs when the cooling capacity of the thermodynamic medium becomes greater than the capacity required to condense the coolant in condenser 42 .

Under these conditions, the excess cooling capacity of the thermodynamic medium can be used to collect additional regeneration heat from the amount of thermal energy that might be rejected from the system as waste heat through return conduit 48.

In the embodiment shown in FIG.
a has an additional and changed transmission arrangement for the cooling part of this subsystem. More particularly, after fluid from external cooling source 24 leaves absorber 67, the fluid is directed to condenser 42a to cool the coolant vapor. With this procedure, the cooling fluid leaving condenser 42a has most of the waste heat rejected by the entire system.

Fluid containing this waste heat flows through transport conduit 56 to regenerative heat exchanger 54 . The waste heat built-in fluid is transferred to the condenser/
Cooling is provided by a thermodynamic medium channeled into the flow path between evaporator 68 and vapor condenser 64 . This operation retains a significant amount of waste heat in the cooling fluid within the cold engine system and also causes the cooling fluid leaving through return conduit 48 to be at a temperature that is significantly different than the temperature of external cooling source 24. Become. This allows for greater effective control of the temperature at which waste heat leaves the cold engine system.

FIG. 6 shows another embodiment of the invention. In this embodiment, certain elements of the absorption-cooling subsystem 23b are integrated with the engine cycle function. Heat input to the low temperature engine system is provided by a low thermal energy input source 2 through steam outlet 27 to generator 45b and steam condenser 64b.
given by 1. The spent steam is returned to the boiler by a return pump 66.

In this example, the thermodynamic medium and the coolant &
A common fluid flows through the low temperature heat engine 22 and the absorption-cooling subsystem 23b. Absorption-cooling sub-device 23
The absorbent in b may typically have the same composition as the more diluted form of the coolant. As these various liquids flow into each other, it is appropriate to view the flow in terms of strong and weak solutions. A strong solution or cooling thermodynamic medium solution has a higher coolant concentration than a weak solution or absorbent. A typical solution could be ammonia as the cooling thermodynamic medium and water as the absorbent.

The strong solution in generator 45b flows through heat transfer member 35b and is heated by the filtered steam. At this time, the strong solution is partially distilled to drive the cooling-thermodynamic medium at high temperature and pressure for expansion and for driving the low temperature thermal engine 22. As the vapor phase of the cooling-thermodynamic medium passes through the outlet 66 to the absorber 37b, its pressure decreases and its temperature decreases.

In the absorber 37b, cold steam enters and mixes, for example by atomization. The weak returning solution enters absorber 37b producing a somewhat cooler, somewhat more concentrated, stronger solution. The solution is further cooled by flow from external cooling source 24 through heat transfer element 47b and through return conduit 48. This cold strong solution is recompressed by pump 41b. At this point, the strong bath liquid becomes a compressed cold fluid that enters the heat exchanger 55. In this heat exchanger 55 the strong solution is heated before returning through conduit 56 to generator 45b.

As a partial distillation process in generator 45b, the weak solution falls into steam condenser 34b and as a stream of hot weak solution to and through heat exchanger 55 for heating the incoming strong solution. It leaves the steam condenser filter 41) through the outlet 57. The weak solution leaves heat exchanger 55 at a lower temperature than the temperature at which it entered. It's a spray
Preferably, the pressure reducing valve 52 is passed through something like a head 58 to enter the absorber 37b.

The following examples more accurately illustrate the invention and suggest the best manner in which it may be carried out, as well as the advantages and improvements realized thereby.

EXAMPLE 1 A cryogenic engine system according to FIG.
It has a mixture of ammonia and water as the cooling solution. The temperature in the condenser is OT and the pressure of the thermodynamic medium is 31.2 psia.

The absorption-cooling subsystem provides a -10'F synthetic sink. The peak temperature for the low temperature turbine of the engine equipment is 210
Steam is supplied from a conventional high pressure steam turbine so as to be ``F''. The external cooling source is 85T cooling tower water.

A high pressure turbine providing a low grade thermal energy input source is
[l'undamentals of C1assic
a+Thermodynamics J+Van
Wylen, Sonntag.

1”ohn Wiley & 5oz + 196E
A basic conventional steam power plant turbine with a cycle as described in L pag 280. The heat pressure cycle itself is summarized as follows. Steam enters the high pressure turbine at 1265 psia and 955" F, 9th steam is extracted at the first extraction point at 330 psia, and 9% steam is extracted at 1' 30 ps at the second extraction point.
ia, the steam of 6.4 is extracted at the 6th extraction point, 48,
Extract at 5 psia and vapors exit at atmospheric pressure. This cycle takes approximately 280 minutes of steam leaving the boiler.
Converts 5 BTU/1 b into mechanical shaft power.

In the generator of a low-temperature engine installation, a strong solution of 21
35% ammonia at a temperature of 0"F and 150 psia. In the absorber, the weak solution is heated to 80"F,
It is 15 psia and 60 part ammonia. The specific heat of the solution is approximately 1.05 BTU/1 b/''F. In supplementary heat exchanger 51, the incoming weak solution from generator 45 is approximately 210'F, while the incoming weak solution from absorber 67 is at approximately 210'F. The incoming strong bath liquid is approximately 8[]"F' and the weak bath liquid exits therefrom at 90"F'.For 6.5 pounds of weak solution in the tuna, the heat transferred from the weak solution is 819 BTU, which means that the strength of the strong bath liquid increases by 1 degree to 104″F′. Therefore, the temperature of the strong solution entering generator 45 is approximately 184°F.

Within generator 45, 1.125 bonds f) g heat transfer energy is required as input to crack each pound of ammonia within generator 45. Condenser/evaporator 38
In , the temperature difference between the thermodynamic medium and ammonia is 2D"F, and the vaporization conditions of ammonia are -20 below, 1
5 psia, and the concentration condition of the thermodynamic medium is O″F′
, 61.16 psia.

The total heat absorption or cooling capacity of ammonia is 558 BTU/
1b and approximately 6 pounds of thermodynamic medium is condensed for each pound of ammonia.

In the heat exchanger or condenser 42, the temperature difference between the exhaust ammonia liquid and the incoming thermodynamic medium liquid is 10"F, and the heat transferred to the thermodynamic medium in this condenser 42 is 66"F.
It is 1 BTU.

In the superheater or steam condenser 64, the thermodynamic medium exiting therefrom is at a pressure of 380 psia at 210"F. The exit conditions for the thermodynamic medium from the pump 41 are 380 psia at 210"F.
It is 80 psia. This means that the required total heat input to the thermodynamic medium is about 119 BTU/IL+ or about 704 BTU for 6 pounds of thermodynamic medium.

Therefore, the heat input required by superheater 64 is 7
04 BTU - 661 BTU, or approximately 43 BTU. This consumes approximately 1.055 pounds of steam in the superheater. Total steam input required for superheater and generator 45
Combined with the heat required to decompose the ammonia within, the total steam input required is 1.18 Bonds.

The dynamic fluid at the inlet point of the low temperature heat engine 22 is at 210"F' and 380 psia, and the outlet temperature is O".
F', 63.7 psia, and the total turbine yield is about 24.7 B i' [J per pound of thermodynamic medium, or about 6 pounds of thermodynamic medium for 1.18 bonds of steam. In contrast, it is approximately 1468 TU. Therefore, for each pound of steam leaving the boiler of a high temperature turbine, the turbine yields approximately 1.18 pounds of steam to 146
It is divided into BTUs, or about 12413 TIJ.

Therefore, the total power output of both the low-temperature engine system according to the Agency and the high-pressure turbine 1) is 280.5 BTU from the high 1-E turbine and 1248 TU from the low-temperature engine system according to the present invention. 404.513 TU per pound.

Comparison A: To illustrate the advantages afforded by the present invention, 220
10.81) A fourth extraction point of steam in the overall high pressure turbine and low pressure turbine of 7,7% steam extracted at Sla. Make a comparison. Steam exits the low pressure turbine and enters the standard condenser at a condenser pressure of 1.5 inches l-I 9-absolute. In this conventional cycle, 33.5 BTtJ for every pound of steam leaving the boiler is converted to shaft power by a low pressure steam turbine.

This makes a total output for this "full steam" conventional device of 280.5 BTU + 63.5 BTU. That is, a total of 314B per pound of steam generated.
i”U.This is Fundamentalsof
C1assical Thermodynamics
This is the complete device for infants described in . Therefore, in this example, 404.58 TU for 1 pound of total loading power provided by the device according to the invention is: f)
514 for 1 pound given by conventional equipment
288 coefficient σ) improvement over BTtJ.

〈Soft B〉 To further illustrate for comparison purposes, Freon lt-11 (
The use of a low-pressure turbine for a combined cycle with a ``bottoming cycle'' (using a thermodynamic medium of the trademark). This I, at a temperature of about 240T and 1
4.7 psiaσ) Receive heat input from the steam exhaust leaving the high pressure steam turbine at a force of Next, bottoming Φ
The cycle was carried out with a turbine inlet pressure of 100 psia and 21
Operating with this thermodynamic medium at a temperature of 0"F, the discharge to the condenser will be at a pressure of 23 psia and 10,570 degrees Celsius. This is due to the cooling water supply from the cooling tower to the condenser at 85 degrees Fahrenheit. This results in the same condenser outlet temperature as that used in the steam low pressure turbine of Comparison A, which was based on
Each pound of steam that leaves the boiler and flows to the high pressure steam turbine produces about 101.5 BTU of low pressure turbine output. That is, the low pressure turbine and i.4. σ) For combined items σ) Total 3-8Z per pound
B. Become T'U. When compared to the full steam system of Comparison A, it yields a power improvement of 2t, &5-.

In this example, the device according to the invention is approximately 5.6
, 2) has an output advantage over the Comparative B device. .

<Example Dragon> The low-temperature engine system shown in FIG. 6 is devised to use ammonia as a thermodynamic medium circulating in an ammonia turbine, and includes an absorber/condenser that receives the turbine exhaust air at the bottom of the turbine cycle σ. Use. turbine 2
The peak temperature for 2 will be 210"F", the external cooling source will be cooling tower water at 850"F", and the combined suction provided by absorption-cooling subsystem 23b will be 110"F".
temperature.

The ammonia vapor flowing into the turbine 22 is at 210'F,
150 psia, while the outlet is -20°F,
It is 15psi. The total power provided by this low temperature engine system is 96.4 BTU per pound of steam leaving the boiler and entering the high pressure steam turbine. 2B0.5
In addition to the power provided by the BTU high pressure steam turbine, the total power of this entire device is 376.9
It becomes BTU/1b. This provides a power improvement of about 20 factors over the Comparative A full steam system. This is approximately the same amount of output improvement as the alternative σ) device B described in Example I.

It is important to note that the cold engine device according to this embodiment does not face the constraints of another device B. This is a sum based on the lowest outside air cooling water temperature that can be supplied by the external cooling rack.

The apparatus of this embodiment can be easily modified by providing an absorption-cooling temperature of less than that of this embodiment with a total cooling input less than that required to reduce the temperature of the external cooling source.

[Brief explanation of the drawing]

FIG. 1 is a schematic plan view showing an embodiment of a low-temperature engine device according to the present invention. FIG. 2 is a schematic plan view of another embodiment of the invention that further minimizes net waste heat rejection to the outside world. FIG. 6 is a schematic plan view showing another embodiment of the invention in which certain features are made integrally. 21: Low-temperature thermal energy source, 22: Low-temperature heat engine, 26: Absorption-cooling sub-device, 24: External cooling source,
25: Steam turbine, 26: High temperature and high pressure steam input, 2
82 generators, 29: generators, 66: return pumps, 6
4: condenser, 67: absorber, 68: condenser/evaporator, 42: condenser, 45: generator, 51: supplementary heat exchanger. Patent applicant: Synthetic Think (4 others) Purification of the drawings (no barbarism in the content) 26 ``Ni-mutual''? Kazuo Sugi 1, Incident Showa (1 year patent application No. Cf-372-5' No. 2,
Name of the invention 2 Enso 7th Section 6, Relationship with the case of the person making the amendment Patent applicant address 2 輻 Shin Uti 7) Shin 2 4, Agent

Claims (1)

[Scope of Claims] (1) Apparatus for supplying a long flow of thermal energy to a low temperature engine system and a circulating absorber for receiving a continuous flow of low temperature heat suction and synthesizing at a selected temperature - an absorber with a cooling solution; - a cooling subsystem and a low temperature heat engine having a circulating thermodynamic medium coupled in heat exchange relationship with the thermal energy input device; an external cooling source for providing a cooling fluid coupled in heat exchange relationship with a cooling solution, the low temperature heat engine having a hot end for flowing a thermodynamic medium coupled in heat exchange relationship with the thermal energy input device; An improvement characterized in that the cold heat engine operates across a thermal gradient and has a cold end into which a thermodynamic medium flows prior to heat exchange coupling with the combined cold heat sink of the absorption-cooling subsystem. low temperature engine equipment. (2) the external cooling source is at outside temperature, and
The apparatus according to claim fi+, characterized in that the low-temperature heat suction is at a degree σ"h':A degrees below the outside air humidity. Claim fi1 is characterized in that it provides a heat source with a temperature higher than the temperature at which it enters the low-temperature heat engine.
Equipment described in Section. (4) Claim fi, wherein the thermal energy input device is discarded from a steam turbine.
The device according to item 1. (5) the low temperature heat engine is a power turbine;
The thermodynamic medium has a vaporization temperature lower than the temperature of steam at the same pressure.
The device described in item 1). (6) The cooling vapor circulating through the absorption-cooling subsystem provides a low heat sink to the circulating thermodynamic medium, and the circulating absorption-cooling solution alternately transfers heat to the circulating thermodynamic medium. Claim No. 1 (1) characterized in that
The device according to item 1. (7) The absorption-cooling subsystem includes an absorber arrangement that incorporates a flow of absorption solution into the flow of engine thermodynamic medium to the absorption-cooling solution. The device described in paragraph (1). (8) The coolant flowing through the absorption-cooling subsystem is:
Apparatus according to claim 1, characterized in that it is coupled in heat exchange relationship with a condenser/vaporizer for condensing an engine thermodynamic medium and vaporizing a coolant. (9) the absorption-cooling subsystem having a condenser that increases the temperature of the circulating engine thermodynamic medium before entering the low temperature heat engine, the condenser decreasing the temperature of the circulating cooling solution; Device according to claim fi+, characterized in that: t+ti Apparatus according to claim 1, characterized in that the absorption-cooling subsystem comprises a generator for separating the absorption-cooling solution into an absorption solution stream and a cooling solution stream. . 0υ the absorber structure includes the low temperature engine device;
Claim 7, characterized in that the structure is coupled in a heat exchange relationship with a circulating fluid to an external cooling source that reduces the temperature of an absorption-cooling solution circulating through the structure. equipment. U. The fluid of the external cooling source is coupled in a circulating heat exchange relationship with the thermodynamic medium of a low temperature heat engine that transfers heat from the circulating cooling fluid to the circulating thermodynamic medium. The device according to section il+. 0j The absorption-cooling subsystem is characterized in that it comprises a generator/condenser that receives thermal energy from the thermal energy input device and separates the absorption-cooling solution into a coolant vapor and a weak solution. An apparatus according to claim (1). 1. Apparatus according to claim 0, characterized in that coolant vapor becomes the engine thermodynamic medium at the hot end of the cold heat engine. 13. Haze: The absorption-cooling subsystem includes an absorber arrangement that intersects the weak bath liquid stream and the coolant vapor stream. ([0) Providing a flow of thermal energy input from a thermal energy source to a cold engine device; Directing a flow of cooling fluid from an external cooling source; A continuous stream of low-temperature heat is generated by heat exchange coupling between a stream of thermal energy and between an absorption-cooling solution and a flow of cooling fluid from an external gIS cooling source. synthesizing the storage at a selected temperature, the synthesis step including providing an absorption-cooling subsystem, a hot end coupled in heat exchange relationship with a flow of thermal energy input, and a continuous flow cold heat storage and heat exchange relationship; providing a heat engine having a flow of a thermodynamic medium operating across a thermal gradient having a cold end coupled with a A method according to claim 1, characterized in that the absorption-cooling solution stream is alternately combined and separated between a stream of a solution with a solute mass and a stream of a solution with a dilute solute mass. tta+ the external cooling source is outside temperature, and
17. A method according to claim 16, characterized in that the selected temperature of the cold heat intake is below the ambient temperature. H. The method according to claim 6), characterized in that the thermodynamic medium has a vaporization temperature lower than the temperature of steam at the same pressure. (2Q) The synthesis step is characterized in that it includes alternately cooling an absorption-cooling solution that provides low-temperature heat absorption and alternately heating an absorption-cooling solution that provides heat to a circulating thermodynamic medium. (21) The flow of coolant and the flow of thermodynamic medium condense the coolant and vaporize the thermodynamic medium after it leaves the heat engine. A method according to claim 1, characterized in that the flow of the coolant and the flow of the thermodynamic medium reduce the temperature of the coolant and the flow of the thermodynamic medium. 9. A method according to claim 0, characterized in that the media interact with each other by a heat exchange coupling that increases the temperature of the medium before entering the heat engine. (23) Said orientation is a step. comprising flowing a cooling fluid coupled in a heat exchange relationship to a flow of the thermodynamic medium before the thermodynamic medium enters the heat engine to transfer heat from the circulating cooling fluid to the circulating thermodynamic medium; The method according to claim α0, characterized in that the synthesis step includes alternating the absorption-cooling solution stream and separating it between a weak solution stream and a strong solution stream. The method according to claim 4, characterized in that (2) the synthesis step comprises partially distilling the absorption-cooling solution stream into a strong cooling vapor stream and a weak solution stream. The method according to claim (16), characterized in that: